EP1715143A2 - Camshaft phasing device for an internal combustion engine - Google Patents

Camshaft phasing device for an internal combustion engine Download PDF

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Publication number
EP1715143A2
EP1715143A2 EP06003222A EP06003222A EP1715143A2 EP 1715143 A2 EP1715143 A2 EP 1715143A2 EP 06003222 A EP06003222 A EP 06003222A EP 06003222 A EP06003222 A EP 06003222A EP 1715143 A2 EP1715143 A2 EP 1715143A2
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EP
European Patent Office
Prior art keywords
adjusting
shaft
gear
designed
camshaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP06003222A
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German (de)
French (fr)
Other versions
EP1715143A3 (en
EP1715143B1 (en
Inventor
Jens Dipl.-Ing. Schäfer
Jonathan Dipl.-Ing. Heywood
Martin Dipl.-Ing. Steigerwald
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Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
Schaeffler KG
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Application filed by Schaeffler Technologies AG and Co KG, Schaeffler KG filed Critical Schaeffler Technologies AG and Co KG
Publication of EP1715143A2 publication Critical patent/EP1715143A2/en
Publication of EP1715143A3 publication Critical patent/EP1715143A3/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/352—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using bevel or epicyclic gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/352—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using bevel or epicyclic gear
    • F01L2001/3521—Harmonic drive of flexspline type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/03—Auxiliary actuators
    • F01L2820/032—Electric motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H2001/2881—Toothed gearings for conveying rotary motion with gears having orbital motion comprising two axially spaced central gears, i.e. ring or sun gear, engaged by at least one common orbital gear wherein one of the central gears is forming the output
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H35/00—Gearings or mechanisms with other special functional features
    • F16H35/008—Gearings or mechanisms with other special functional features for variation of rotational phase relationship, e.g. angular relationship between input and output shaft

Definitions

  • the invention relates to a device for the electrical adjustment of the relative angular position between a camshaft and a crankshaft of an internal combustion engine, with an adjusting gear, which has a crankshaft fixed drive member, a camshaft fixed output member and an adjusting shaft of an electric adjustment rotatably connected adjusting shaft.
  • An electric camshaft adjuster of this kind is from the DE 102 48 355 A1 known.
  • an adjusting device for electrically adjusting the relative rotational angle position between the camshaft and the crankshaft wherein a three-shaft gearbox is used as adjusting, which has a crankshaft fixed drive part, a camshaft fixed output part and a rotationally fixed to a Verstellmotorwolle an electric adjusting motor connected adjusting shaft.
  • the adjusting motor is designed here as a brushless DC motor with a stator fixed to the housing and a permanent magnet rotor.
  • As adjustment a double eccentric gear or a double planetary gear is used, in which case a reduction up to 1: 250 is provided.
  • the relative displacement of the camshaft to the crankshaft is also described in other documents, with equally adjusting gears are used, which can be actuated by an electric motor.
  • the EP 1 039 101 A2 uses a Harmonic Drive gearbox as the variable speed gearbox. This gear works with a thin, elastically deformable, toothed sleeve, the toothing of the sleeve meshes with a ring gear. For a compact design of the variable speed is possible with a large reduction ratio.
  • the US 5,680,836 and the DE 102 03 621 A1 uses a planetary gear as adjusting gear to produce the relative rotation between the crankshaft and camshaft. Such a solution is also from the DE 25 25 746 A1 known.
  • the power flow should be able to take place during the adjustment with a high efficiency in order to build the driving electric motor or the braking device as small as possible.
  • the lowest possible heat loss should arise.
  • the teeth of the variable speed gear should run as free of play as possible. If this is not the case, unwanted high noise occurs during operation, the cause of which is primarily in the highly variable alternating torque of the camshaft. If necessary, occurring in the adjusting gear games are converted according to the transmission ratio of the transmission.
  • certain distances between the body and the internal combustion engine must be maintained, which equally requires a compact engine design.
  • the adjustment must be possible cost can be realized so that the system cost of the electric camshaft adjuster, consisting of adjusting, electric motor / brake and control electronics, can be kept low.
  • the present invention is therefore based on the object , a camshaft adjuster of the type mentioned in such a way that a smoother running of the variable speed is also possible if there are teeth or concentricity error.
  • the production costs should be kept low without this having a negative effect on the running behavior of the variable transmission.
  • the solution of this problem by the invention is characterized in that the adjusting shaft of the adjusting gear is mounted or arranged radially floating.
  • the adjusting is not stored in the true sense, it is rather radially within certain limits freely displaced and centers itself on the meshing of the meshing gears.
  • a coupling is preferably arranged between the adjusting shaft and the adjusting unit shaft, which permits a slight relative radial displacement between the adjusting shaft and the adjusting unit shaft. While the adjusting shaft in the electric motor or the braking device, which are fixedly connected to the internal combustion engine, is radially mounted, the radial bearing is not transmitted to the adjusting shaft due to the radial flexibility of the clutch; this is rather radially movable relative to the adjustment shaft.
  • the adjustment unit may be as an electric motor or an electric brake device be educated
  • the coupling is preferably an elastomeric coupling or Oldham coupling used.
  • the adjusting mechanism is designed according to one embodiment as a double planetary gear.
  • the double planetary gear may have two adjacently arranged internal gears, with which at least one, two or more spur gears, preferably three spur gears, combing or combing simultaneously, wherein the number of teeth of the two internal gears is different and wherein the number of teeth corresponds to the number of spur gears or a multiple thereof ,
  • the at least one spur gear can be mounted in a planet carrier, which in particular itself acts as an adjusting shaft.
  • the at least one spur gear can be mounted by means of a roller bearing in the planet carrier; In principle, this is also a sliding bearing in question.
  • the at least one two or more spur gears can also be made for the at least one two or more spur gears to mesh with a centrally arranged sun gear, which is connected to the adjusting shaft (the so-called Wolfrom gear).
  • the adjustment can also be designed as a double eccentric or corrugated transmission.
  • the amount of the reduction of the variable-speed transmission is preferably between 1: 2 to 1: 250.
  • this preferably has high-inductance permanent magnet rotors.
  • the Adjusting shaft parts can compensate for a part of the backlash due to their radial mobility, for example due to concentricity errors, which leads to a quieter run. As a result, the operating noise is reduced, as well as the risk of clamping in tooth engagement.
  • a further advantage is that the radial bearing of the adjusting of the adjusting or the adjusting shaft associated parts of the transmission can be omitted, which not only reduces the friction of the variable, but also makes the transmission cheaper. Due to the lower friction, the efficiency of the transmission can be increased.
  • Fig. 1 is a schematic diagram can be seen, showing the basic structure of a camshaft adjuster, which is equipped with an electrically driven variable speed.
  • the camshaft adjustment device 1 serves to adjust the camshaft 2 of an internal combustion engine relative to its crankshaft in order to influence the valve timing.
  • an adjusting mechanism 3 is provided, which has a crankshaft-fixed drive part 4 and a camshaft-fixed output part 5.
  • the crankshaft fixed drive part 4 has a sprocket 16, wherein a chain, not shown, the firm rotational connection to the crankshaft produces.
  • the adjusting mechanism 3 has an adjusting shaft 8 as an input shaft, which is non-rotatably connected via a coupling 9 to an adjusting shaft 6, wherein the adjusting shaft 6 is part of an electric adjusting unit 7, for example an electric motor or a braking device. Since the adjusting mechanism 3 is designed as a summation gear, a rotation of the adjusting shaft 8 by means of the adjusting 7 with the result that a relative rotation between the crankshaft fixed drive member 4 and camshaft-fixed output member 5 is accomplished, so that the camshaft timing between a "early stop” and a "late stop” can be changed.
  • the adjusting shaft 8 is connected to a planet carrier 13, over whose circumference a number of spur gears 12 are arranged with an external toothing.
  • the planet carrier 13 ensures that the required center distance between the spur gears is maintained.
  • crankshaft fixed drive member 4 and the camshaft fixed output member 5 each have a ring gear-like teeth 10 and 11, with which the spur gears 12 mesh with their teeth.
  • the two internal gears 10, 11 have an unequal number of teeth. The difference of the teeth is the number of used for the front wheels 12 or a Many of them.
  • the tooth difference between the teeth 10 and 11 is 2, 4, 6, etc. If three spur gears 12 are provided, the difference of the teeth 3, 6, 9, etc.
  • the adjustment can be performed with a positive or a negative reduction ratio.
  • the spur gears 12 are formed so wide that they simultaneously with the internal teeth 10 and the internal teeth 11 mesh.
  • the planet carrier 13 itself is not additionally stored radially, as is common in the solutions according to the prior art. He centered by the interventions of the teeth of the spur gears 12 and the drive or driven parts 4, 5 automatically, wherein it is arranged floating with respect to the radial direction. This can be compensated in an improved manner gear errors, resulting in a quieter running of the variable transmission 3.
  • the coupling 9 is designed as a radially flexible coupling. It allows a slight radial movement between the two shaft parts 6 and 8.
  • the clutch 9 thus ensures that small Deviations of the adjusting shaft 8 are compensated in the radial direction, while at the same time transmits the adjustment torque.
  • Examples of such couplings are elastomer couplings or Oldham couplings, which as such are well known.
  • Fig. 2 shows an embodiment of the invention, in which a double planetary gear is used as adjusting.
  • the bearing of the spur gears 12 in the planet carrier 13 may be formed as a rolling or sliding bearing.
  • Rolling bearings 14 are used in the exemplary embodiment, which results in low friction.
  • the planet carrier 13 has no axial contact surfaces, but the entire planet carrier unit is guided axially over the side walls of the spur gears. This avoids that friction due to the axial system acts directly on the planet carrier 13 and thus on the electric adjustment unit 7, which would result in a deterioration of the efficiency.
  • the coupling 9 is designed as an elastomer coupling. In the recess 17 shown in Fig. 2 engages a coupling part, not shown, which is connected to the adjusting shaft (not shown).
  • the coupling 9 permits a slight radial movement between the adjusting unit shaft and the part of the coupling designated by the reference numeral 8.
  • the planet carrier 13 is arranged radially floating.
  • the adjusting gear is designed as a Wolfrom gear, ie as a gearbox to be allocated to the type of planetary gear.
  • the adjusting gear has two mutually mounted ring gears with the internal gears 10 and 11, which are again connected to the crankshaft and the camshaft.
  • the difference in the number of teeth between the teeth 10 and 11 must be as large as the number of spur gears 12 and a multiple thereof.
  • the adjustment of the adjusting gear takes place here with a sun gear 15 which is in engagement with all spur gears 12 and which is arranged radially floating again.
  • the difference to a Wolfromgetriebe previously known as such is that the sun gear 15 and the spur gears 12 (planet gears) are positioned radially only via the meshing.
  • the Oldham coupling 9 here as such a well-known Oldham coupling is provided. It should again be noted that here too, the adjusting shaft 8 is or is formed as a part together with a portion of the coupling 9. Also, the Oldham coupling 9 allows a slight radial movement between the Verstellinheitswelle and the reference numeral 8 provided part of the coupling.
  • a corrugated gear can be used as adjusting 3.
  • the harmonic drive works and the harmonic drive transmission, which as such is well known, work on the same principle.
  • the camshaft-fixed output part 5 has an internal toothing 11, while the crankshaft-fixed drive part 4 has the internal toothing 10. Both teeth 10, 11 are connected to an externally toothed thin-walled sleeve 18 in engagement.
  • the here elliptically shaped adjusting shaft 8 leads to engagement of the teeth 10 and 11 with the outer teeth of the sleeve 18 at two opposite circumferential locations of the sleeve 18. Upon rotation of the adjusting shaft 8 by means of Verstellinheitwelle (not shown), it comes therefore to the reduction effect of the wave gear ,
  • the adjusting shaft 8 is connected to a coupling 9, which in the present case by the use of elastomeric material 19, the floating according to the invention Arrangement of the adjusting 8 causes.
  • the marked in Fig. 4 by the reference numeral 20 radial region of the adjusting shaft 8 together with adjacent components is therefore arranged floating, ie the centering takes place without radial bearing exclusively by the meshing.
  • any types of adjusting gear 3 can be used to realize the inventive concept. Mention should be made, for example, known swash plate mechanism or the non-uniform translating slider crank mechanism.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Retarders (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Abstract

The device has an adjustment gear unit with a drive part (4) that is fixed in a crankshaft, an output part (5) that is fixed in a camshaft and an adjustment shaft (8) that is connected with an adjustment mechanism shaft in a torque proof manner. The adjustment shaft is arranged in a radially rolling manner. A coupler (9) allows radial adjustment between the adjustment shaft and the adjustment mechanism shaft.

Description

Gebiet der ErfindungField of the invention

Die Erfindung betrifft eine Vorrichtung zur elektrischen Verstellung der relativen Drehwinkellage zwischen einer Nockenwelle und einer Kurbelwelle einer Brennkraftmaschine, mit einem Verstellgetriebe, das ein kurbelwellenfestes Antriebsteil, ein nockenwellenfestes Abtriebsteil und eine mit einer Verstelleinheitswelle einer elektrischen Verstelleinheit drehfest verbundene Verstellwelle aufweist.The invention relates to a device for the electrical adjustment of the relative angular position between a camshaft and a crankshaft of an internal combustion engine, with an adjusting gear, which has a crankshaft fixed drive member, a camshaft fixed output member and an adjusting shaft of an electric adjustment rotatably connected adjusting shaft.

Hintergrund der ErfindungBackground of the invention

Zur relativen Verstellung der Winkelstellung zwischen der Kurbelwelle und der Nockenwelle eines Verbrennungsmotors sind im Stand der Technik verschiedene Möglichkeiten bekannt. Grundsätzlich sind elektrische und hydraulische Verstellsysteme bekannt. Bei den elektrisch angetriebenen Nockenwellenverstellsystemen gilt es, das relativ niedrige Drehmoment der elektrischen Verstelleinheit, beispielsweise eines Antriebsmotors oder einer Bremsvorrichtung, das bei hoher Drehzahl zur Verfügung steht, in eine Drehbewegung mit hohem Drehmoment zu wandeln; ein solches hohes Drehmoment ist für die Verstellung der Nockenwelle nötig. Hierfür ist es bekannt, Summiergetriebe als Verstellgetriebe einzusetzen. Ein solches Getriebe weist ein kurbelwellenfestes Antriebsrad auf. Der Abtrieb erfolgt über einen nockenwellenfesten Getriebeabgang. Die Differenzleistung des Getriebes, die zur Verstellung in die eine oder andere Drehrichtung eingekoppelt werden muss, wird über eine dritte Welle, die Verstellwelle, des Getriebes eingeleitet.For relative adjustment of the angular position between the crankshaft and the camshaft of an internal combustion engine, various possibilities are known in the prior art. Basically, electrical and hydraulic adjustment systems are known. In the case of the electrically driven camshaft adjusting systems, the relatively low torque of the electrical adjusting unit, For example, a drive motor or a braking device, which is available at high speed to convert into a rotational movement with high torque; Such a high torque is necessary for the adjustment of the camshaft. For this purpose it is known to use summing as adjustment. Such a transmission has a crankshaft-fixed drive wheel. The output takes place via a camshaft-fixed gearbox outlet. The differential power of the transmission, which must be coupled for adjustment in one or the other direction of rotation, is introduced via a third shaft, the adjusting shaft of the transmission.

Ein elektrischer Nockenwellenversteller dieser Art ist aus der DE 102 48 355 A1 bekannt. Offenbart ist eine Verstellvorrichtung zum elektrischen Verstellen der relativen Drehwinkellage zwischen der Nockenwelle und der Kurbelwelle, wobei ein Dreiwellengetriebe als Verstellgetriebe zum Einsatz kommt, das ein kurbelwellenfestes Antriebsteil, ein nockenwellenfestes Abtriebsteil und eine mit einer Verstellmotorwolle eines elektrischen Verstellmotors drehfest verbundenen Verstellwelle aufweist. Der Verstellmotor ist hier als bürstenloser Gleichstrommotor mit einem gehäusefesten Stator und einem Dauermagnetrotor ausgebildet. Als Verstellgetriebe kommt ein Doppelexzentergetriebe bzw. ein Doppelplanetengetriebe zum Einsatz, wobei hier eine Untersetzung bis zu 1:250 vorgesehen ist.An electric camshaft adjuster of this kind is from the DE 102 48 355 A1 known. Disclosed is an adjusting device for electrically adjusting the relative rotational angle position between the camshaft and the crankshaft, wherein a three-shaft gearbox is used as adjusting, which has a crankshaft fixed drive part, a camshaft fixed output part and a rotationally fixed to a Verstellmotorwolle an electric adjusting motor connected adjusting shaft. The adjusting motor is designed here as a brushless DC motor with a stator fixed to the housing and a permanent magnet rotor. As adjustment a double eccentric gear or a double planetary gear is used, in which case a reduction up to 1: 250 is provided.

Die Relativverstellung der Nockenwelle zur Kurbelwelle wird auch in anderen Druckschriften beschrieben, wobei gleichermaßen Verstellgetriebe zum Einsatz kommen, die von einem Elektromotor betätigt werden können. Die EP 1 039 101 A2 setzt als Verstellgetriebe ein Harmonic-Drive-Getriebe ein. Dieses Getriebe arbeitet mit einer dünnen, elastisch verformbaren, verzahnten Hülse, wobei die Verzahnung der Hülse mit einem Hohlrad kämmt. Damit ist eine kompakte Bauart des Verstellgetriebes bei einem großen Untersetzungsverhältnis möglich.The relative displacement of the camshaft to the crankshaft is also described in other documents, with equally adjusting gears are used, which can be actuated by an electric motor. The EP 1 039 101 A2 uses a Harmonic Drive gearbox as the variable speed gearbox. This gear works with a thin, elastically deformable, toothed sleeve, the toothing of the sleeve meshes with a ring gear. For a compact design of the variable speed is possible with a large reduction ratio.

Eine solche Lösung ist auch aus der DE 40 22 735 A1 bekannt, bei der ein solches Zykloid-Untersetzungsgetriebe zum Einsatz kommt. Eine ähnliche Bauart zeigt die WO 95/00748 . Such a solution is also from the DE 40 22 735 A1 known, in which such a cycloid reduction gear is used. A similar Design shows the WO 95/00748 ,

Die US 5,680,836 und die DE 102 03 621 A1 setzt ein Planetengetriebe als Verstellgetriebe ein, um die Relativdrehung zwischen Kurbel- und Nockenwelle zu erzeugen. Eine solche Lösung ist auch aus der DE 25 25 746 A1 bekannt.The US 5,680,836 and the DE 102 03 621 A1 uses a planetary gear as adjusting gear to produce the relative rotation between the crankshaft and camshaft. Such a solution is also from the DE 25 25 746 A1 known.

Der Leistungsfluss soll dabei während der Verstellung mit einem hohen Wirkungsgrad erfolgen können, um den antreibenden Elektromotor oder die Bremsvorrichtung möglichst klein bauen zu können. Dabei soll eine möglichst geringe Verlustwärme entstehen. Weiterhin sollen die Verzahnungen des Verstellgetriebes möglichst spielfrei zueinander laufen. Ist dies nicht der Fall, entstehen während des Betriebs unerwünscht hohe Geräusche, deren Ursache primär in dem stark veränderlichen Wechseldrehmoment der Nockenwelle liegt. Gegebenenfalls im Verstellgetriebe auftretende Spiele werden entsprechend dem Übersetzungsverhältnis des Getriebes gewandelt. Zusätzlich ist es notwendig, den Bauraum für den Drehmomentwandler so klein wie möglich zu gestalten, da ein Trend zu immer kompakterer Bauweise des Verbrennungsmotors besteht. Ferner sind aus sicherheitstechnischen Gründen gewisse Abstände zwischen der Karosserie und dem Verbrennungsmotor einzuhalten, was gleichermaßen eine kompakte Motorbauart erfordert. Darüber hinaus muss das Verstellgetriebe möglichst kostengünstig realisiert werden können, damit die Systemkosten für den elektrischen Nockenwellenversteller, bestehend aus Verstellgetriebe, Elektromotor / Bremse und Ansteuerelektronik, gering gehalten werden können.The power flow should be able to take place during the adjustment with a high efficiency in order to build the driving electric motor or the braking device as small as possible. Here, the lowest possible heat loss should arise. Furthermore, the teeth of the variable speed gear should run as free of play as possible. If this is not the case, unwanted high noise occurs during operation, the cause of which is primarily in the highly variable alternating torque of the camshaft. If necessary, occurring in the adjusting gear games are converted according to the transmission ratio of the transmission. In addition, it is necessary to make the space for the torque converter as small as possible, since there is a trend towards ever more compact design of the internal combustion engine. Furthermore, for safety reasons, certain distances between the body and the internal combustion engine must be maintained, which equally requires a compact engine design. In addition, the adjustment must be possible cost can be realized so that the system cost of the electric camshaft adjuster, consisting of adjusting, electric motor / brake and control electronics, can be kept low.

Bei den vorbekannten Lösungen gibt es diesbezüglich Einschränkungen, insbesondere, was die Laufruhe anbelangt. Rundlauffehler der zum Einsatz kommenden Verzahnungen sind nur mit hohem Aufwand gering zu halten, so dass beim Eingriff der Zahnräder und bei deren Rotation eine gewisse Geräuschentwicklung unvermeidlich ist. Je geringer der kostentreibende Fertigungsaufwand bei der Herstellung der zum Einsatz kommenden Zahnräder ist, desto größer wird das Problem der Geräuschentwicklung.In the known solutions, there are restrictions in this regard, especially as far as the smoothness is concerned. Run-out of the gears used are to be kept low only with great effort, so that a certain noise is unavoidable when engaging the gears and their rotation. The lower the costly manufacturing effort in the production of the gears used, the greater the problem of noise.

Aufgabe der ErfindungObject of the invention

Der vorliegenden Erfindung liegt daher die Aufgabe zugrunde, einen Nockenwellenversteller der eingangs genannten Art so fortzubilden, dass eine höhere Laufruhe des Verstellgetriebes auch dann möglich ist, wenn Verzahnungs- bzw. Rundlauffehler vorliegen. Damit sollen die Herstellkosten gering gehalten werden können, ohne dass sich dies negativ auf das Laufverhalten des Verstellgetriebes auswirkt.The present invention is therefore based on the object , a camshaft adjuster of the type mentioned in such a way that a smoother running of the variable speed is also possible if there are teeth or concentricity error. Thus, the production costs should be kept low without this having a negative effect on the running behavior of the variable transmission.

Zusammenfassung der ErfindungSummary of the invention

Die Lösung dieser Aufgabe durch die Erfindung ist dadurch gekennzeichnet, dass die Verstellwelle des Verstellgetriebes radial schwimmend gelagert bzw. angeordnet ist.The solution of this problem by the invention is characterized in that the adjusting shaft of the adjusting gear is mounted or arranged radially floating.

Im Gegensatz zu den bekannten Lösungen wird also die Verstellwelle im eigentlichen Sinne gar nicht mehr gelagert, sie ist vielmehr radial in gewissen Grenzen frei verschiebbar und zentriert sich selber über den Zahneingriff der kämmenden Zahnräder.In contrast to the known solutions, so the adjusting is not stored in the true sense, it is rather radially within certain limits freely displaced and centers itself on the meshing of the meshing gears.

Bevorzugt ist zwischen der Verstellwelle und der Verstelleinheitswelle hierzu eine Kupplung angeordnet, die eine geringfügige relative radiale Verschiebung zwischen der Verstellwelle und der Verstelleinheitswelle zulässt. Während die Verstelleinheitswelle im Elektromotor oder der Bremsvorrichtung, welche fest mit dem Verbrennungsmotor verbunden sind, radial gelagert ist, wird die radiale Lagerung aufgrund der radialen Flexibilität der Kupplung nicht auf die Verstellwelle übertragen; diese ist vielmehr relativ zur Verstelleinheitswelle radial beweglich.For this purpose, a coupling is preferably arranged between the adjusting shaft and the adjusting unit shaft, which permits a slight relative radial displacement between the adjusting shaft and the adjusting unit shaft. While the adjusting shaft in the electric motor or the braking device, which are fixedly connected to the internal combustion engine, is radially mounted, the radial bearing is not transmitted to the adjusting shaft due to the radial flexibility of the clutch; this is rather radially movable relative to the adjustment shaft.

Die Verstelleinheit kann als ein elektrischer Motor oder eine elektrische Bremsvorrichtung ausgebildet sein
Als Kupplung kommt bevorzugt eine Elastomerkupplung oder eine Oldham-Kupplung zum Einsatz.The adjustment unit may be as an electric motor or an electric brake device be educated
The coupling is preferably an elastomeric coupling or Oldham coupling used.

Das Verstellgetriebe ist nach einer Ausgestaltung als Doppelplanetengetriebe ausgebildet. Das Doppelplanetengetriebe kann zwei benachbart angeordnete Innenverzahnungen aufweisen, mit denen mindestens ein, zwei oder mehrere Stirnräder, vorzugsweise drei Stirnräder, gleichzeitig kämmt bzw. kämmen, wobei die Zähnezahl der beiden Innenverzahnungen unterschiedlich ist und wobei die Zähnezahldifferenz der Anzahl der Stirnräder oder einem Vielfachen davon entspricht.The adjusting mechanism is designed according to one embodiment as a double planetary gear. The double planetary gear may have two adjacently arranged internal gears, with which at least one, two or more spur gears, preferably three spur gears, combing or combing simultaneously, wherein the number of teeth of the two internal gears is different and wherein the number of teeth corresponds to the number of spur gears or a multiple thereof ,

Das mindestens eine Stirnrad kann in einem Planetenträger gelagert sein, wobei dieser insbesondere selber als Verstellwelle fungiert. Das mindestens eine Stirnrad kann mittels einer Wälzlagerung in dem Planetenträger gelagert sein; grundsätzlich kommt hierzu aber auch eine Gleitlagerung in Frage.The at least one spur gear can be mounted in a planet carrier, which in particular itself acts as an adjusting shaft. The at least one spur gear can be mounted by means of a roller bearing in the planet carrier; In principle, this is also a sliding bearing in question.

Gemäß einer alternativen Bauart kann auch vorgesehen sein, dass das mindestens eine zwei oder mehrere Stirnräder mit einem zentral angeordneten Sonnenrad kämmt, das mit der Verstellwelle verbunden ist (das so genannte Wolfromgetriebe).According to an alternative design, provision can also be made for the at least one two or more spur gears to mesh with a centrally arranged sun gear, which is connected to the adjusting shaft (the so-called Wolfrom gear).

Das Verstellgetriebe kann auch als Doppelexzentergetriebe oder Wellgetriebe ausgebildet sein.The adjustment can also be designed as a double eccentric or corrugated transmission.

Der Betrag der Untersetzung des Verstellgetriebes vorzugsweise zwischen 1:2 bis 1:250 liegt. Bei Einsatz eines Motors als elektrische Verstelleinheit weist dieser vorzugsweise hochinduktive Dauermagnetrotoren auf.The amount of the reduction of the variable-speed transmission is preferably between 1: 2 to 1: 250. When using a motor as an electrical adjustment unit, this preferably has high-inductance permanent magnet rotors.

Durch die vorgeschlagene Lösung ergibt sich der Vorteil, dass sich die Verstellwelle des Verstellgetriebes bzw. dass sich die verstellwellengebundenen Teile des Getriebes - aufgrund der schwimmenden Lagerung - optimal zu den Zahnrädern zentriert bzw. zentrieren, mit denen sie kämmt bzw. kämmen. Die Verstellwellenteile können durch ihre radiale Beweglichkeit einen Teil des Verdrehflankenspiels, beispielsweise aufgrund von Rundlauffehlern, ausgleichen, was zu einem ruhigeren Lauf führt. Dadurch wird das Betriebsgeräusch reduziert, gleichermaßen die Gefahr von Klemmungen im Zahneingriff.Due to the proposed solution, there is the advantage that the adjusting shaft of the variable-speed gear or that the adjusting shaft-bonded parts of the transmission - due to the floating bearing - optimally centered or centered with the gears with which it combs or comb. The Adjusting shaft parts can compensate for a part of the backlash due to their radial mobility, for example due to concentricity errors, which leads to a quieter run. As a result, the operating noise is reduced, as well as the risk of clamping in tooth engagement.

Von Vorteil ist weiterhin, dass die radiale Lagerung der Verstellwelle des Verstellgetriebes bzw. der verstellwellengebundenen Teile des Getriebes entfallen kann, was nicht nur die Reibung des Verstellgetriebes reduziert, sondern das Getriebe auch preiswerter macht. Durch die geringere Reibung lässt sich der Wirkungsgrad des Getriebes erhöhen.A further advantage is that the radial bearing of the adjusting of the adjusting or the adjusting shaft associated parts of the transmission can be omitted, which not only reduces the friction of the variable, but also makes the transmission cheaper. Due to the lower friction, the efficiency of the transmission can be increased.

Ebenfalls positiv zu vermerken ist, dass der benötigte Bauraum des Getriebes reduziert werden kann.Another positive thing to note is that the space required for the gearbox can be reduced.

Kurze Beschreibung der FigurenBrief description of the figures

In den Zeichnungen sind Ausführungsbeispiele der Erfindung dargestellt. Es zeigen:

Fig. 1
eine schematische Darstellung eines Nockenwellenverstellers, der mit einem elektrisch angetriebenen Verstellgetriebe versehen ist,
Fig. 2
eine teilweise geschnittene perspektivische Darstellung eines Nockenwellenverstellers, bei dem das Verstellgetriebe als Doppelplanetengetriebe ausgebildet ist,
Fig. 3
eine teilweise geschnittene perspektivische Darstellung eines Nockenwellenverstellers, bei dem das Verstellgetriebe als Wolfromgetriebe ausgebildet ist, und
Fig. 4
den Radialschnitt durch einen Nockenwellenversteller, bei dem das Verstellgetriebe als Wellgetriebe ausgebildet ist.
In the drawings, embodiments of the invention are shown. Show it:
Fig. 1
a schematic representation of a camshaft adjuster, which is provided with an electrically driven adjusting gear,
Fig. 2
a partially sectioned perspective view of a camshaft adjuster, in which the adjusting gear is designed as a double planetary gear,
Fig. 3
a partially sectioned perspective view of a camshaft adjuster, in which the adjusting gear is designed as Wolfromgetriebe, and
Fig. 4
the radial section through a camshaft adjuster, in which the adjusting gear is designed as a wave gear.

Ausführliche Beschreibung der FigurenDetailed description of the figures

In Fig. 1 ist eine Prinzipskizze zu sehen, die den grundsätzlichen Aufbau eines Nockenwellenverstellers zeigt, der mit einem elektrisch angetriebenen Verstellgetriebe ausgestattet ist. Die Vorrichtung 1 zur Nockenwellenverstellung dient dazu, die Nockenwelle 2 eines Verbrennungsmotors relativ zu seiner Kurbelwelle zu verstellen, um die Ventilsteuerzeiten zu beeinflussen. Hierzu ist ein Verstellgetriebe 3 vorgesehen, das ein kurbelwellenfestes Antriebsteil 4 und ein nockenwellenfestes Abtriebsteil 5 aufweist. Schematisch ist angedeutet, dass das kurbelwellenfeste Antriebsteil 4 ein Kettenrad 16 hat, wobei eine nicht dargestellte Kette die feste Drehverbindung zur Kurbelwelle herstellt.In Fig. 1 is a schematic diagram can be seen, showing the basic structure of a camshaft adjuster, which is equipped with an electrically driven variable speed. The camshaft adjustment device 1 serves to adjust the camshaft 2 of an internal combustion engine relative to its crankshaft in order to influence the valve timing. For this purpose, an adjusting mechanism 3 is provided, which has a crankshaft-fixed drive part 4 and a camshaft-fixed output part 5. Schematically it is indicated that the crankshaft fixed drive part 4 has a sprocket 16, wherein a chain, not shown, the firm rotational connection to the crankshaft produces.

Das Verstellgetriebe 3 hat als Eingangswelle eine Verstellwelle 8, die über eine Kupplung 9 mit einer Verstelleinheitswelle 6 drehfest verbunden ist, wobei die Verstelleinheitswelle 6 Bestandteil einer elektrischen Verstelleinheit 7, beispielsweise eines Elektromotors oder einer Bremsvorrichtung, ist. Da das Verstellgetriebe 3 als Summiergetriebe gestaltet ist, hat eine Drehung der Verstellwelle 8 mittels der Verstelleinheit 7 zur Folge, dass eine Relativdrehung zwischen kurbelwellenfestem Antriebsteil 4 und nockenwellenfestem Abtriebsteil 5 bewerkstelligt wird, so dass die Nockenwellensteuerzeiten zwischen einen "Frühanschlag" und einem "Spätanschlag" verändert werden können.The adjusting mechanism 3 has an adjusting shaft 8 as an input shaft, which is non-rotatably connected via a coupling 9 to an adjusting shaft 6, wherein the adjusting shaft 6 is part of an electric adjusting unit 7, for example an electric motor or a braking device. Since the adjusting mechanism 3 is designed as a summation gear, a rotation of the adjusting shaft 8 by means of the adjusting 7 with the result that a relative rotation between the crankshaft fixed drive member 4 and camshaft-fixed output member 5 is accomplished, so that the camshaft timing between a "early stop" and a "late stop" can be changed.

Die Verstellwelle 8 ist mit einem Planetenträger 13 verbunden, über dessen Umfang eine Anzahl Stirnräder 12 mit einer Außenverzahnung angeordnet sind. Der Planetenträger 13 sorgt dafür, dass der benötigte Achsabstand zwischen den Stirnrädern eingehalten wird.The adjusting shaft 8 is connected to a planet carrier 13, over whose circumference a number of spur gears 12 are arranged with an external toothing. The planet carrier 13 ensures that the required center distance between the spur gears is maintained.

Das kurbelwellenfeste Antriebsteil 4 sowie das nockenwellenfeste Abtriebsteil 5 weisen je eine hohlradartig ausgebildete Verzahnungen 10 bzw. 11 auf, mit denen die Stirnräder 12 mit ihren Verzahnungen kämmen. Die beiden Innenverzahnungen 10, 11 haben dabei eine ungleiche Zähnezahl. Die Differenz der Zähne ist dabei die Anzahl der zum Einsatz kommenden Stirnräder 12 oder ein Vielfaches davon.The crankshaft fixed drive member 4 and the camshaft fixed output member 5 each have a ring gear-like teeth 10 and 11, with which the spur gears 12 mesh with their teeth. The two internal gears 10, 11 have an unequal number of teeth. The difference of the teeth is the number of used for the front wheels 12 or a Many of them.

Kommen beispielsweise zwei Stirnräder 12 zum Einsatz, beträgt die Zahndifferenz zwischen den Verzahnungen 10 und 11 2, 4, 6, usw. Sind drei Stirnräder 12 vorgesehen, beträgt die Differenz der Zähne 3, 6, 9, usw.For example, if two spur gears 12 are used, the tooth difference between the teeth 10 and 11 is 2, 4, 6, etc. If three spur gears 12 are provided, the difference of the teeth 3, 6, 9, etc.

Abhängig davon, welches Zahnrad 10, 11 die größere Zähnezahl aufweist, kann das Verstellgetriebe mit einem positiven oder einem negativen Untersetzungsverhältnis ausgeführt werden.Depending on which gear 10, 11 has the larger number of teeth, the adjustment can be performed with a positive or a negative reduction ratio.

Wie zu sehen ist, sind die Stirnräder 12 so breit ausgebildet, dass sie gleichzeitig mit der Innenverzahnung 10 und der Innenverzahnung 11 kämmen.As can be seen, the spur gears 12 are formed so wide that they simultaneously with the internal teeth 10 and the internal teeth 11 mesh.

Aufgrund der unterschiedlichen Zähnezahl zwischen den beiden Verzahnungen 10, 11 ergibt sich, dass bei Drehantrieb der Verstellwelle 8 und damit bei Rotation des Planetenträgers 13 eine Relativbewegung zwischen den beiden Verzahnungen 10 und 11 hervorgerufen wird, die eine starke Untersetzung aufweist. Typische Untersetzungen liegen bei 1:50 bis 1:200.Due to the different number of teeth between the two gears 10, 11 results in that upon rotation of the adjusting shaft 8 and thus upon rotation of the planet carrier 13, a relative movement between the two gears 10 and 11 is caused, which has a strong reduction. Typical ratios are 1:50 to 1: 200.

Erfindungswesentlich ist, dass der Planetenträger 13 selbst nicht zusätzlich radial gelagert wird, wie es bei den Lösungen gemäß dem Stand der Technik üblich ist. Er zentriert sich durch die Eingriffe der Verzahnungen der Stirnräder 12 und der Antriebs- bzw. Abtriebsteile 4, 5 selbsttätig, wobei er hinsichtlich der radialen Richtung schwimmend angeordnet ist. Damit können in verbesserter Weise Verzahnungsfehler ausgeglichen werden, was zu einem geräuschärmeren Lauf des Verstellgetriebes 3 führt.Essential to the invention is that the planet carrier 13 itself is not additionally stored radially, as is common in the solutions according to the prior art. He centered by the interventions of the teeth of the spur gears 12 and the drive or driven parts 4, 5 automatically, wherein it is arranged floating with respect to the radial direction. This can be compensated in an improved manner gear errors, resulting in a quieter running of the variable transmission 3.

Aufgrund der schwimmenden Bewegung des Planetenträgers 13 kann eine kleine Achsabweichung zwischen dem Planetenträger 13 und der Verstelleinheitswelle 6 entstehen. Aus diesem Grunde ist die Kupplung 9 als radial flexible Kupplung ausgelegt. Sie erlaubt eine geringfügige radiale Bewegung zwischen den beiden Wellenteilen 6 und 8. Die Kupplung 9 sorgt also dafür, dass kleine Abweichungen der Verstellwelle 8 in radialer Richtung ausgeglichen werden, während sie gleichzeitig das Verstelldrehmoment überträgt. Beispiele solcher Kupplungen sind Elastomerkupplungen oder Oldham-Kupplungen, die als solche hinlänglich bekannt sind.Due to the floating movement of the planet carrier 13, a small axis deviation between the planet carrier 13 and the adjustment unit shaft 6 can arise. For this reason, the coupling 9 is designed as a radially flexible coupling. It allows a slight radial movement between the two shaft parts 6 and 8. The clutch 9 thus ensures that small Deviations of the adjusting shaft 8 are compensated in the radial direction, while at the same time transmits the adjustment torque. Examples of such couplings are elastomer couplings or Oldham couplings, which as such are well known.

Fig. 2 zeigt eine Ausführungsform der Erfindung, bei der ein Doppelplanetengetriebe als Verstellgetriebe zum Einsatz kommt. Die Lagerung der Stirnräder 12 im Planetenträger 13 kann als Wälz- oder Gleitlagerung ausgebildet sein. Im Ausführungsbeispiel kommen Wälzlagerungen 14 zum Einsatz, was eine niedrige Reibung zur Folge hat.Fig. 2 shows an embodiment of the invention, in which a double planetary gear is used as adjusting. The bearing of the spur gears 12 in the planet carrier 13 may be formed as a rolling or sliding bearing. Rolling bearings 14 are used in the exemplary embodiment, which results in low friction.

Zur Reibungsminimierung hat der Planetenträger 13 keine axialen Anlageflächen, sondern die gesamte Planetenträgereinheit wird über die Seitenwände der Stirnräder axial geführt. Dadurch wird vermieden, dass Reibung aufgrund der axialen Anlage direkt auf den Planetenträger 13 und somit auf die elektrische Verstelleinheit 7 wirkt, was eine Verschlechterung des Wirkungsgrades zur Folge hätte.To minimize friction, the planet carrier 13 has no axial contact surfaces, but the entire planet carrier unit is guided axially over the side walls of the spur gears. This avoids that friction due to the axial system acts directly on the planet carrier 13 and thus on the electric adjustment unit 7, which would result in a deterioration of the efficiency.

Zu erwähnen ist bei der Lösung gemäß Fig. 2 noch, dass die Verstellwelle 8 hier als ein Teil zusammen mit einem Abschnitt der Kupplung 9 ausgebildet ist bzw. fungiert. Die Kupplung 9 ist als Elastomerkupplung ausgebildet. In die in Fig. 2 dargestellte Ausnehmung 17 greift ein nicht dargestelltes Kupplungsteil ein, das mit der (nicht dargestellten) Verstelleinheitswelle verbunden ist. Die Kupplung 9 erlaubt eine geringfügige radiale Bewegung zwischen der Verstelleinheitswelle und dem mit der Bezugsziffer 8 versehenen Teil der Kupplung. Damit ist der Planetenträger 13 radial schwimmend angeordnet.To mention is in the solution according to FIG. 2 nor that the adjusting shaft 8 is formed here as a part together with a portion of the coupling 9 and acts. The coupling 9 is designed as an elastomer coupling. In the recess 17 shown in Fig. 2 engages a coupling part, not shown, which is connected to the adjusting shaft (not shown). The coupling 9 permits a slight radial movement between the adjusting unit shaft and the part of the coupling designated by the reference numeral 8. Thus, the planet carrier 13 is arranged radially floating.

Gemäß der Ausgestaltung nach Fig. 3 ist vorgesehen, dass das Verstellgetriebe als Wolfromgetriebe ausgeführt ist, d. h. als ein der Gattung der Planetengetriebe zuzurechnendes Getriebe. Das Verstellgetriebe weist zwei zueinander gelagerte Hohlräder mit den Innenverzahnungen 10 und 11 auf, die wieder mit der Kurbelwelle bzw. mit der Nockenwelle verbunden sind. Weiterhin besteht wieder gleichzeitiger Zahneingriff mit mehreren Stirnrädern 12. Wie beim Doppelplanetengetriebe muss auch hier wieder der Unterschied der Zähnezahl zwischen den Verzahnungen 10 und 11 so groß sein wie die Anzahl der Stirnräder 12 bzw. einem Vielfachen davon. Die Verstellung des Verstellgetriebes erfolgt hier mit einem Sonnenrad 15, das mit allen Stirnrädern 12 im Eingriff ist und das wieder radial schwimmend angeordnet ist. Der Unterschied zu einem als solchen vorbekannten Wolfromgetriebe besteht also darin, dass das Sonnenrad 15 und die Stirnräder 12 (Planetenräder) nur über die Zahneingriffe radial positioniert werden.According to the embodiment according to FIG. 3, it is provided that the adjusting gear is designed as a Wolfrom gear, ie as a gearbox to be allocated to the type of planetary gear. The adjusting gear has two mutually mounted ring gears with the internal gears 10 and 11, which are again connected to the crankshaft and the camshaft. Continue to exist Again, simultaneous meshing with multiple spur gears 12. As with the double planetary gear again here the difference in the number of teeth between the teeth 10 and 11 must be as large as the number of spur gears 12 and a multiple thereof. The adjustment of the adjusting gear takes place here with a sun gear 15 which is in engagement with all spur gears 12 and which is arranged radially floating again. The difference to a Wolfromgetriebe previously known as such is that the sun gear 15 and the spur gears 12 (planet gears) are positioned radially only via the meshing.

Als Kupplung 9 ist hier eine als solche hinlänglich bekannte Oldham-Kupplung vorgesehen. Es ist wieder anzumerken, dass auch hier die Verstellwelle 8 als ein Teil zusammen mit einem Abschnitt der Kupplung 9 ausgebildet ist bzw. fungiert. Auch die Oldham-Kupplung 9 erlaubt eine geringfügige radiale Bewegung zwischen der Verstelleinheitswelle und dem mit der Bezugsziffer 8 versehenen Teil der Kupplung.As a coupling 9 here as such a well-known Oldham coupling is provided. It should again be noted that here too, the adjusting shaft 8 is or is formed as a part together with a portion of the coupling 9. Also, the Oldham coupling 9 allows a slight radial movement between the Verstellinheitswelle and the reference numeral 8 provided part of the coupling.

Wie Fig. 4 zeigt, kann statt eines Planetengetriebes auch beispielsweise ein Wellgetriebe als Verstellgetriebe 3 zum Einsatz kommen. Das Wellgetriebe arbeitet und das Harmonic-Drive-Getriebes, das als solches hinlänglich bekannt ist, arbeiten nach dem gleichen Prinzip.As Fig. 4 shows, instead of a planetary gear, for example, a corrugated gear can be used as adjusting 3. The harmonic drive works and the harmonic drive transmission, which as such is well known, work on the same principle.

Das nockenwellenfeste Abtriebsteil 5 weist eine Innenverzahnung 11 auf, während das kurbelwellenfeste Antriebsteil 4 die Innenverzahnung 10 hat. Beide Verzahnungen 10, 11 stehen mit einer außenverzahnten dünnwandigen Hülse 18 im Eingriff. Die hier elliptisch ausgeformte Verstellwelle 8 führt zum Eingriff der Verzahnungen 10 bzw. 11 mit der Außenverzahnung der Hülse 18 an zwei sich gegenüberliegenden Umfangsstellen der Hülse 18. Bei Drehung der Verstellwelle 8 mittels der Verstelleinheitswelle (nicht dargestellt) kommt es daher zu dem Untersetzungseffekt des Wellgetriebes.The camshaft-fixed output part 5 has an internal toothing 11, while the crankshaft-fixed drive part 4 has the internal toothing 10. Both teeth 10, 11 are connected to an externally toothed thin-walled sleeve 18 in engagement. The here elliptically shaped adjusting shaft 8 leads to engagement of the teeth 10 and 11 with the outer teeth of the sleeve 18 at two opposite circumferential locations of the sleeve 18. Upon rotation of the adjusting shaft 8 by means of Verstellinheitwelle (not shown), it comes therefore to the reduction effect of the wave gear ,

Die Verstellwelle 8 ist mit einer Kupplung 9 verbunden, die vorliegend durch den Einsatz von Elastomermaterial 19 die erfindungsgemäße schwimmende Anordnung der Verstellwelle 8 bewirkt. Der in Fig. 4 mit dem Bezugszeichen 20 markierte radiale Bereich der Verstellwelle 8 samt angrenzender Bauteile ist daher schwimmend angeordnet, d. h. die Zentrierung erfolgt ohne Radiallagerung ausschließlich durch die Zahneingriffe.The adjusting shaft 8 is connected to a coupling 9, which in the present case by the use of elastomeric material 19, the floating according to the invention Arrangement of the adjusting 8 causes. The marked in Fig. 4 by the reference numeral 20 radial region of the adjusting shaft 8 together with adjacent components is therefore arranged floating, ie the centering takes place without radial bearing exclusively by the meshing.

Grundsätzlich können beliebige Arten von Verstellgetrieben 3 zum Einsatz kommen, um das Erfindungskonzept zu realisieren. Erwähnt seien beispielsweise an sich bekannte Taumelscheibengetriebe oder das ungleichförmig übersetzende Schubkurbelgetriebe.In principle, any types of adjusting gear 3 can be used to realize the inventive concept. Mention should be made, for example, known swash plate mechanism or the non-uniform translating slider crank mechanism.

Bezugszeichenliste:LIST OF REFERENCE NUMBERS

11
Vorrichtung zur NockenwellenverstellungCamshaft adjustment device
22
Nockenwellecamshaft
33
Verstellgetriebevariator
44
kurbelwellenfestes Antriebsteilcrankshaft resistant drive part
55
nockenwellenfestes AbtriebsteilCamshaft-fixed output part
66
Verstelleinheitswelleadjustment-
77
elektrische Verstelleinheitelectric adjustment unit
88th
Verstellwelleadjusting
99
Kupplungclutch
1010
Innenverzahnunginternal gearing
1111
Innenverzahnunginternal gearing
1212
Stirnradspur gear
1313
Planetenträgerplanet carrier
1414
Wälzlagerungroller bearing
1515
Sonnenradsun
1616
KettenradSprocket
1717
Ausnehmungrecess
1818
Hülseshell
1919
Elastomermaterialelastomeric material
2020
radialer Bereichradial area

Claims (15)

Vorrichtung (1) zur elektrischen Verstellung der relativen Drehwinkellage zwischen einer Nockenwelle (2) und einer Kurbelwelle einer Brennkraftmaschine, mit einem Verstellgetriebe (3), das ein kurbelwellenfestes Antriebsteil (4), ein nockenwellenfestes Abtriebsteil (5) und eine mit einer Verstelleinheitswelle (6) einer elektrischen Verstelleinheit (7) drehfest verbundene Verstellwelle (8) aufweist, dadurch gekennzeichnet, dass die Verstellwelle (8) radial schwimmend angeordnet ist.Device (1) for the electrical adjustment of the relative angular position between a camshaft (2) and a crankshaft of an internal combustion engine, with a variable speed gearbox (3) comprising a camshaft-fixed drive part (4), a camshaft-fixed driven part (5) and an adjusting shaft (6 ) of an electric adjusting unit (7) rotatably connected adjusting shaft (8), characterized in that the adjusting shaft (8) is arranged radially floating. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass zwischen der Verstellwelle (8) und der Verstelleinheitswelle (6) eine Kupplung (9) angeordnet ist, die eine geringfügige relative radiale Verschiebung zwischen der Verstellwelle (8) und der Verstelleinheitswelle (6) zulässt.Apparatus according to claim 1, characterized in that between the adjusting shaft (8) and the adjusting unit shaft (6) a coupling (9) is arranged, which allows a slight relative radial displacement between the adjusting shaft (8) and the adjusting unit shaft (6). Vorrichtung nach Anspruch 2, dadurch gekennzeichnet, die Verstelleinheit 7 als ein elektrischer Motor oder eine elektrische Bremsvorrichtung ausgebildet ist.Apparatus according to claim 2, characterized in that the adjusting unit 7 is designed as an electric motor or an electric braking device. Vorrichtung nach Anspruch 2, dadurch gekennzeichnet, dass die Kupplung (9) als Elastomerkupplung ausgebildet ist.Apparatus according to claim 2, characterized in that the coupling (9) is designed as an elastomer coupling. Vorrichtung nach Anspruch 2, dadurch gekennzeichnet, dass die Kupplung (9) als Oldham-Kupplung ausgebildet ist.Apparatus according to claim 2, characterized in that the coupling (9) is designed as Oldham coupling. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass das Verstellgetriebe (3) als Doppelplanetengetriebe ausgebildet ist.Apparatus according to claim 1, characterized in that the adjusting mechanism (3) is designed as a double planetary gear. Vorrichtung nach Anspruch 6, dadurch gekennzeichnet, dass das Doppelplanetengetriebe (3) zwei benachbart angeordnete Innenverzahnungen (10, 11) aufweist, mit denen mindestens ein Stirnrad (12) gleichzeitig kämmt, wobei die Zähnezahl der beiden Innenverzahnungen (10, 11) unterschiedlich ist und wobei die Zähnezahldifferenz der Anzahl der Stirnräder (12) oder einem Vielfachen davon entspricht.Apparatus according to claim 6, characterized in that the double planetary gear (3) has two adjacently arranged internal gears (10, 11) with which at least one spur gear (12) meshes simultaneously, wherein the number of teeth of the two internal gears (10, 11) is different and wherein the number of teeth difference corresponds to the number of spur gears (12) or a multiple thereof. Vorrichtung nach Anspruch 7, dadurch gekennzeichnet, dass das mindestens eine Stirnrad (12) in einem Planetenträger (13) gelagert ist.Apparatus according to claim 7, characterized in that the at least one spur gear (12) in a planet carrier (13) is mounted. Vorrichtung nach Anspruch 8, dadurch gekennzeichnet, dass der Planetenträger (13) als Verstellwelle (8) fungiert.Apparatus according to claim 8, characterized in that the planet carrier (13) acts as an adjusting shaft (8). Vorrichtung nach Anspruch 8, dadurch gekennzeichnet, dass das mindestens eine Stirnrad (12) mittels einer Wälzlagerung (14) in dem Planetenträger (13) gelagert ist.Apparatus according to claim 8, characterized in that the at least one spur gear (12) by means of a rolling bearing (14) is mounted in the planet carrier (13). Vorrichtung nach Anspruch 7, dadurch gekennzeichnet, dass das mindestens eine Stirnrad (12) mit einem zentral angeordneten Sonnenrad (15) kämmt, das mit der Verstellwelle (8) verbunden ist oder als Verstellwelle (8) fungiert.Apparatus according to claim 7, characterized in that the at least one spur gear (12) meshes with a centrally arranged sun gear (15) which is connected to the adjusting shaft (8) or acts as adjusting shaft (8). Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass das Verstellgetriebe (3) als Doppelexzentergetriebe ausgebildet ist.Apparatus according to claim 1, characterized in that the adjusting mechanism (3) is designed as a double eccentric gear. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass das Verstellgetriebe (3) als Wellgetriebe ausgebildet ist.Apparatus according to claim 1, characterized in that the adjusting mechanism (3) is designed as a wave gear. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass der Betrag der Untersetzung das Verstellgetriebes (3) zwischen 1:2 bis 1:250 liegt.Device according to claim 1, characterized in that the amount the reduction ratio of the variable transmission (3) is between 1: 2 to 1: 250. Vorrichtung nach Anspruch 3, dadurch gekennzeichnet, dass die elektrische Verstelleinheit (7) als Motor ausgebildet ist, der hochinduktive Dauermagnetrotoren aufweist.Apparatus according to claim 3, characterized in that the electrical adjustment unit (7) is designed as a motor having high-inductance permanent magnet rotors.
EP06003222A 2005-04-23 2006-02-17 Camshaft phasing device for an internal combustion engine Revoked EP1715143B1 (en)

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DE102005018956A DE102005018956A1 (en) 2005-04-23 2005-04-23 Device for adjusting the camshaft of an internal combustion engine

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JP2006300068A (en) 2006-11-02
KR101267138B1 (en) 2013-05-23
US20060236965A1 (en) 2006-10-26
US7506623B2 (en) 2009-03-24
JP5100028B2 (en) 2012-12-19
DE102005018956A1 (en) 2006-11-23
EP1715143A3 (en) 2009-11-18
EP1715143B1 (en) 2012-06-20
KR20060111396A (en) 2006-10-27

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